DE2806843A1 - METHOD AND SYSTEM FOR CONVERTING THERMAL ENERGY INTO MECHANICAL ENERGY - Google Patents

Description

KENNETH A. WILLIAMS

Belleair Shores, Florida (V.St.A.)

Method and system for converting
Thermal energy into mechanical energy

The invention relates to a system for

Generating mechanical energy, in particular a method and a device for converting thermal energy into
me chani see before energy.

It is well known that the world’s supplies of common fuels such as natural gas, Gl, coal and
the like, can be consumed quickly. The continued supply of these fuels has been around for some
Seriously questioned for years. The fuels mentioned are used for numerous purposes, but perhaps none of them is more important than the generation of thermal energy, which is converted into mechanical energy to drive land and water vehicles, and into electrical energy
can be converted for household and industrial use. Sahi-rich other energy sources are also available or are in the process of being developed, e.g. B, solar energy, nuclear energy and the like, and
These alternative energy sources will, to the extent that they are used, meet the current and anticipated difficulties in fuel supply
mitigate. It should be borne in mind, however, that nuclear energy
is expensive and their recovery too enormous and so far

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unsolved environmental problems leads to "The conversion of solar energy into mechanical energy is still in the development stage and cannot be practiced at least at the moment in all climatic areas, especially in areas with frequent occurrences of cloudiness ₉ fog or smog" Thus there is currently no really usable energy source available ₉ which can be used in place of conventional fuels to meet the ever increasing demands of modern society for mechanical energy.

Numerous systems have been proposed in which those supplied by conventional energy sources have been proposed Energy with higher efficiency is recovered by the thermodynamisehen and flow losses on one To be reduced to a minimum. Unfortunately, even the systems are unable to increase the efficiency of the Energy conversion will improve considerably su, and they generally do not even allow the maximum utilization the possibilities of energy conversion. For example is a system for conversion in US Pat. No. 3,335S '! -51 the energy of a liquid stream in mechanical ICiieiTcie annc ^ even, whereby 'by heating' a liquid Working means a iiwoiphaenstrom is generated, which accelerated and separated into the liquid and the vapor phase, whereupon the kinetic energy of the liquid phase converted into mechanical work, the vapor phase is condensed into liquid and the liquid flows combined and then reheated. In this system, however, the energy contained in the working fluid not converted into mechanical work as much as possible, and valuable thermal energy is not used, but given in a condenser to a heat exchange medium.

3 -

./Hi.

The object of the invention is therefore

in the creation of a system suitable for generating mechanical energy, in which the energy content of a work medium is used to a greater extent for work performance than was previously possible.

Another object of the invention is

in the creation of a process for generating mechanical energy without consuming or utilizing conventional fuels.

It is also an object of the invention to provide an environmentally friendly method for Generating mechanical energy.

Another object of the invention is to provide a method that can be used to generate mechanical energy from i «poor energy is suited to the is at least partially obtained from ambient energy, for example in the atmosphere, in rivers or Army or as waste heat etc. is available.

Another object of the invention is to provide a method or system that is particularly applicable for cooling and air conditioning and greatly reduces the energy requirement in these applications.

The invention creates a continuous Process and a cycle system to convert thermal energy into mechanical energy, with an evaporator, which has an energy conversion tube with at least one nozzle section and is used to generate a stream of a to convert liquid working medium into a stream, the volume of which is largely or completely

909829/0523

ordered from steam, wherein a current-charged turbine is also provided, which converts part of the steam flow energy into mechanical shaft drive energy, a device for increasing the content of the working fluid flowing out of the turbine of thermal energy and potential energy and for condensing the working fluid to an im essential liquid stream, as well as a device for returning the liquid stream to the evaporator «The system can be used with particular advantage on conventional cooling or heat pump cycle processes in which the usual throttle valve through a throttling-free nozzle and a turbine for intake and recovery the expansion work is replaced. The inventively proposed energy conversion tubes can also be used to drive two-phase flows with large flow rates, for _a B ₀ for safety valves of Drtickgef ate _o

Other tasks, features and benefits

of the subject matter of the invention are explained below with reference to the accompanying drawings

Fig. 1 schematically shows an embodiment of the method and system according to the invention Use of a single flow of working medium <,

Fig. 2 shows an embodiment of one in the invention System of usable energy conversion pipe,

Fig. 3 shows a preferred embodiment of a in the energy conversion tube usable in the system according to the invention,

Fig. H schematically shows the essential elements of a

common mechanical cold steam refrigeration machine,

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y- 1306843

46 ·

Fig. 5 in. A temperature-eritropy diagram that

thermodynamic behavior of the refrigeration machine according to Fig. k,

Fig. 6 shows schematically that modified by adding a nozzle and a turbine according to the invention Refrigeration machine g-emüß Fig. 4 and

Fig. 7 is a temperature-entropy diagram

thermodynamic behavior of the refrigeration machine According to Fig. 6.

Fig. 1 shows a continuously working Ijreisprozesssystesi «to convert the energy potential of the appropriately selected, pressurized working medium into mechanical shaft drive energy, the energy consumed in the system, including line drive energy, is replaced by thermal energy that is taken from an available thermal energy source , which can be formed, for example, by radioisotopes, nuclear reactors, furnaces (in particular furnaces for burning other than usual fuels, e.g. waste incinerator), or solar converters or from ambient energy sources, provided that there is sufficient ambient energy (e.g. in the atmosphere , Rivers, seas, as waste heat, etc.). The system shown only works with one flow of working medium. There are many tools that can be used. In general, any liquid that can work-expand in a cycle is suitable for use. The boiling point and the minimum values for the temperature and pressure in the selected cycle and the evaporation and condensation to be carried out in this must be taken into account. In a system that operates at normal ambient temperature or at a temperature only slightly higher or lower, am is used

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The best low-boiling working media, preferably working media whose boiling point is considerably below the freezing point of water _o Examples of such working media are carbon dioxide, liquid nitrogen and the fluorocarbons _o Usable fluorocarbons are, for example, difluoromonoclilomethane, pentafluoromonochloroethane ₉ difluorodichloromethane and other azeotropic temperatures and systems operating at higher pressures can be used as the working medium water or other known coolants, which also include liquid metals, such as sodium, potassium, mercury and the like, _{or the like}

According to the invention the flow of the working medium is supplied to a device in which the non-kinetic energy of a stream d ₀ h _o its static Druckcnergie, its thermal energy and / or its potential energy is converted into kinetic or G-eschwindigkeitsenergie. This device is hereinafter referred to as the Snergioumwandlungsrohr (EUR) _o In this EUR the speed of the current is increased and fileic! .I2; e: ltif; the static pressure and the temperature of the flow are considerably reduced "When the pressure drops, part of the thermal energy contained in the liquid is released and part of the liquid evaporates." The flow thus obtained has a larger vapor volume ",

In a preferred embodiment of the

Invention, the energy conversion pipe has at least one nozzle section ,, Depending on the nature of the system, in which the EUR is used, it can expediently have several nozzle sections arranged at a longitudinal distance from one another (see Figs. 2 and 3) have, by several

Recovery lines are interconnected. For example, the EUR can have a single nozzle section or a nozzle section and a recovery section or several nozzle sections arranged between these recovery sections. In one of several Stretch existing EUR occurs the work equipment that has a large content of potential or static Possesses energy (is under high static pressure) and is essentially saturated (this will be discussed below defined) into the first nozzle section, in which the working medium is converted into a stream or jet, which has a high speed and a lower pressure and flows axially in the pipe. With the current of the Working fluid through the nozzle section increases the speed due to the narrowing flow cross-section and increases the kinetic energy of the working fluid. ¥ ¥ while the work equipment is accelerating and the drop in its static pressure begins to tap the saturated liquid 211, -by which, a toilet ilu-ex · Y / nioenergy is consumed. As a result, the The stream emerging from the nozzle section has a larger volume, a higher content of kinetic energy, a lower static pressure, lower temperature and a higher vapor content »This creates a liquid is referred to as "substantially saturated" when it is either completely saturated or saturated enough to be under the flow conditions existing in the first nozzle section at least partially evaporated. Particularly preferred are conditions under which the liquid when entering the first nozzle section and preferably also when entering each subsequent nozzle section of the SUR is saturated.

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The aüstretende from the nozzle distance _t fast flowing working medium ,, the liquid from a relatively fast-flowing _ß phase, and a significantly faster flowing vapor phase is "enters a pumping and recovering s tr corner _p in by converting the pulse of the vapor phase dio speed _b the temperature and the static pressure of flüscigen Phaso increased tferden _o to? TIGS © in purpose trird oin ffeil the kinetic and thermal energy of the vapor phase to the liquid phase discharged _e thereby regenerated for the next expansion process in the next distance t? IRDO It is onge = aommen ₉ that, in the pumping and Rückgei-rLnnu & dor gostrecke relatively rapidly flowing steam to the relatively slowly flowing liquid impinges, and in accordance with the momentum conservation takes place a momentum exchange between Flüssiglceit and steam, the velocity of the vapor phase is reduced _o This reduction in velocity is of an increase in the static hen pressure (compression), without the need for external work _o As a result, at least part of the vapor condenses and the latent heat of condensation of this condensed part is given off to the liquid phase and the kinetic energy of the liquid continue to increase, that part of the vapor condenses, that part of the static pressure converted into kinetic energy in the nozzle section is recovered and that the temperature of the working medium is increased to a level which is higher than at the outlet Nozzle section, but lower than at the nozzle section inlet. As a result, the liquid, which is under a higher static pressure and at a higher temperature, can again accelerate and accelerate in the next nozzle section

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1806849 • SO-

.r: no.n.s5.on unt9r ^T ,; orfon TOr ¹ CCn. Iis' - / ird oai ^ eiioKimon ^ da.il dor -'ort scream toric ^: c temperature from ti o ··; the l? Iüssi {Tl-: oii; in the l'ii: vp— and ^ ück ^ ov ^ nnurvys stretch car to the fact that the liquid "! / ülireiid des? uEpvor ;; an st an el i." y with can etauaruci; con Ltauipfss boauf'sc'ila; tt / irci, Diöse; repeated Yerdar.ipfunrrs- and zondensationsvor ^ än ^ e in de «! -inor ^ ieuirroandlun ^ srolir nabon sur Γοΐ-το, clai: · the pre-warning work nods; more or more eiiiksitlick in all liiclitun ^ en acts, but downstairs to the stohenöGii fdauni towards the lower pressure stohenöGii fdauni gelexud T-, ^r ird. As a result, the flowing fluid is subjected to a flow rate, so that the fluid emerging from the thorn tube has a high degree of fluidity and thus possesses a large number of kinetic energy, so that the velocity and the kinetic fluid can flow ; iei'jehalt greater ilolir from the exiting liquid nöiier BSV _t when the Kolrr has not only one but several Düsenstreciccii. When using never-irerei nozzle stretches, inan forner nacii the first nozzle stretch can transfer part of the steam's latent and kinetic energy back to the liquid, in which the heat energy transferred in this way
can be reused and converted into additional kinetic energy. If only a single nozzle section is used, the latent thermal energy content of the
However, steam can only be reused to a lesser extent, so that more thermal energy z. 3. Must be delivered to the air exchange medium in a condenser instead of being used for additional work. This recovery and reuse of latent heat is considered to be an important contribution to the higher
Considered efficiency that can be achieved with the system according to the invention.

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EAD

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! '' if, *, 2 is an energy conversion channel with several nozzle sections for flow velocities in the subsonic range. The liohr 100 includes a plurality of spaced from each other arranged nozzles stretch 102 _s 104, 1o6 _9108, the rdückgewinnungsstrecken each other by a plurality of generally cylindrical 110, 112, 1 1M are connected _o In the embodiment shown in Fijj- _O 3 embodiment, the Snergieurnwandlungsrohr 200 has a plurality of Diffuser sections widening in the longitudinal direction. 210, 212, 214 “In general, diffuser sections are preferably used as suction sections, because these effect a control that helps prevent the static pressure front in the pipe from becoming so low at any point that a? liquid droplets not expanding downstream, but expanding radially _o

Another important feature of the invention is that the linergieumwandlungsrohr also has means to suppress metastable flow conditions in the ear "one can use any suitable means for suppressing metastable flow conditions for this purpose" Electricity, ζ "B _n add a quock-silver current," Mechanical smocks can also be used, κ. 3. stronungsu'-nlonizende elements, such as blades, arranged in spike-flow of the working medium, "to suppress metastable flow conditions one can not mechanically ^ means, such as sound or radio waves apply _o lös has been said that" it is necessary the evaporation of the working medium in a SUR with a single nozzle section or the successive evaporation and condensation

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BATH ORIGINAL

.29.

processes in an SCR with several Jüson- bzv7. Recovery stretches are carried out under regulated conditions, so that the evaporation of the working medium, which is exposed to a low pressure, takes place within the fluid, in which the released heat energy can be absorbed by the liquid and converted into kinetic energy. If the evaporation takes place outside the EUR, as could be the case if the actual evaporation only takes place after the pressure has dropped to the value required for the evaporation, metastable flow conditions are present and the heat energy released does not convert into kinetic energy with good efficiency Energy of the flowing working medium converted. A constant suppression of metastable flow conditions is therefore a very important element of the invention, even in an EUIl with only a single nozzle section. The desired pumping action in the dome and the required flow rate of the liquid are obtained with the best efficiency if one uses nozzle sections arranged at a distance from one another, the pressure in the throat of each nozzle being lower than the pressure in the throat of each upstream thereof arranged nozzle, and the suppression of metastable flow conditions is taken care of, If the 3UTl is operated with flow velocities in the subsonic range, the flow rang ^ squersclmitt of each nozzle section must be smaller than the flow cross section of each upstream of it at _: ^r : oorfi.noi? n Dilseristrocke. At flow velocities in the supersonic range, the flow cross-section of each nozzle section is greater than the flow cross-section of each nozzle section arranged upstream thereof.

In the embodiment according to FIG. 1, any of the working means indicated above can be used.

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The in FIR ₀ 1, "ezeiitG system continuously operates in a Kreisnrozeß In Beschreibunr ange-ηοκποη is that the entry of the Isur 50 is the starting point dos system _o The working medium entering the SUIi 50 is a voi.." Z u ~ sweise saturated liquid with respect to their temperatures and pressures corresponding to a .Jnthalpiegcnalt that is at least as large as that in the system expected jßnergieverbrauch ₉ inclusive of the votes Wellonantx ^ iebsenergieo the? λΐΐϋ.. 50 is a normal nozzle pipe, for example one of the above-described Siiergiemawandlun ^ rohre. When the working fluid passes through the 3UIi 50, the potential, static and thermal energy content of the working fluid is partially converted into kinetic jnex "gio and the speed of the flow is considerable increased, while its static pressure and temperature are reduced considerably. Since the kinetic IDnergie is a function of both the Hasse and the speed may be obtained by adding a sweiten stream z "B ₀ of a mercury current zn, the flow of the working fluid flowing Increase the mass and thereby reduce the flow velocity; without reducing the kinetic energy of the flow. As a result of the addition of the second flow, the total flow has a lower flow velocity. On the other hand, the kinetic energy is kept essentially constant as a result of the increase in mass _o The second flow carries also on the suppression of metastable flow conditions in the DUR ato In the EUR 50 part of the flowing liquid evaporates, so that the flow, which initially consists essentially of liquid, is converted into a flow ₉ the volume of which consists mainly of steam, _etc.

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With the one from the EUIt 50 with relatively holier The speed of the current exiting is directly applied to the impeller of the turbine 52. In the turbine there will be a Part of the kinetic energy of the working fluid is converted into mechanical energy to drive the turbine shaft. You may not be able to enter downstream of the EUR 50 and upstream of the turbine 52 Switch on the throttle valve shown, with which the amount of kinetic energy converted in the turbine is controlled can be.

The working fluid emerging from the turbine has been used up. If the used working medium is to be reused in a continuously operating cycle system, its energy content must be increased. In one embodiment of the invention, the liquid and vapor phases of the working medium emerging from the turbine are separated from one another for this purpose, whereupon the static energy content of each phase is increased and the two phases are combined again. The separation can be carried out by gravity separation, for example by arranging the lines $ k and 56 for drawing off the liquid or the vapor phase vertically one above the other, the liquid line 5h being located below the vapor line 56. The separation of vapor and liquid is further aided by the fact that the vapor line 56 is considerably larger in diameter than the liquid line, for example 10 times as large. With the power delivered by the turbine 52 to its shaft, a steam compressor or a steam pump 58 in the line 60 and a liquid pump in the line 5A are driven, so that the static pressure and

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"*" 28068A3 • US

and the energy content of the vapor phase and the liquid phase can be increased. As a result of the compression of the steam in the pump 58, the steam temperature is increased to a value which is considerably higher than the temperature of the liquid. Downstream of pumps 58 and 60, the liquid and vapor streams are recombined. The cold liquid absorbs heat from the steam, for example by the steam spreading a thin film of the liquid in the usual way, so that the steam condenses immediately and the total flow at the inlet is also via the shaft of the expansion engine with pump 62 driven by this generated energy consists essentially only of liquid. The liquid trace Ö2 brings the static pressure of the liquid to such a high value that the liquid does not evaporate even when heat energy is supplied to the absorber 6k. At the same time, the pump 62 increases the energy content of the working medium.

The pumps 58, bO and 62 also serve to quickly draw off the used working fluid from the turbine. This is necessary so that there is no counter pressure on the turbine that could impair the efficiency of the turbine. Of course, there is no need to use three pumps as in FIG. 2, but the 58-60 pump can be replaced by a single centrifugal pump. In general, any pump arrangement can be used which can perform the two basic functions of the Pximpen 58, 60 and 62, that is to say can draw the exhausted working fluid from the turbine and increase the static pressure and the energy content of the working fluid.

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The liquid that has leaked from the pump 62

is passed through an.Absorber 6k , in which the working fluid is supplied with energy to compensate for the energy consumption due to the conversion of energy into mechanical shaft drive energy in the turbine 52 and due to friction losses and other thermodynamic losses at other points in the system due to energy losses. The absorber 6k should have such a large length or such a large cross-sectional area that it enables the absorption of a predetermined amount of energy. For this purpose, the absorber 6k contains a control device (not shown) for precise control of the amount of energy absorbed. When passing through the absorber 6k , the working medium absorbs so much heat energy that it has the desired energy content. The temperature of the working medium emerging from the pump 62 should be considerably lower than the temperature of the heat source so that the working medium can be brought to the desired energy content by absorbing thermal energy from the heat source. The thermal energy supplied to the working medium must be sufficient to replace the energy consumption which is due to the conversion of energy in the turbine 52 into mechanical shaft drive energy, which is not fed back into the working medium in the pumps 58, 60 and 62, and to energy losses caused by Frictional losses and other thermodynamic losses are caused at other points in the system. Regardless of the type of heat source used, this heat energy must be transferred to the system. Therefore, the choice of a suitable working medium and the pressure and temperature values for a particular system can only be made after the heat source has been selected and the thermal conditions have been defined. That the

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28068Λ3

The working fluid leaving the absorber 64 is in substantially saturated and contains so much energy that the cycle at the inlet nozzle 50 begins again can. To regulate the resulting output power, you can add some thermal energy to the working fluid before static energy is supplied to it.

An embodiment will be described below and the operating conditions for a System specified in which the ambient heat at temperatures in the range of 29 - 38 ° C as a heat source and that commercially available from E.I. du Pont de Nemours & Company, Inc. available Preon 22 as a working tool is used.

Execution example

In the system shown in FIG. 1, Freon (difluoromonochloromethane) was used as the working medium. Below are the values for the energy content of the work equipment at the points indicated on the System as well as the amounts of energy supplied to the system (+) and the energy losses occurring in the system (-) specified in joules per leg of the work equipment »

At the entrance of the EXJR

At the absorber outlet

It is assumed that the working medium is a liquid with not very high viscosity, that the entire energy contained in the working fluid is potential energy, d. H. static and thermal energy, is (hereinafter referred to as PE) and the work equipment has no kinetic energy (hereinafter referred to as IiE)

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-w- 2806841

contains »Then is

PE = 16IOO J / kg
KE = O

At the exit of the EUR

At the turbine entrance

PS = 11300 j / kg
KE = ij-800 J / kg

At the turbine exit

At the inlet of pumps 58 and 6O

PE = 30000 j / kg

With a turbine efficiency of 67 fo , the work done by the working fluid in the turbine is 3200 J / kg. In the absorber

Thermal energy given off by the heat source: + 2000 J / kg

As indicated above, one can

determine the temperature of the working fluid flowing out of the turbine if the temperature of the heat source known and the desired mechanical output power of the turbine has been determined. Because of the temperature of the working medium flowing out of the turbine, a suitable working medium and the minimum values can be selected for the operating pressure and temperature. The system can operate at temperatures or pressures can be operated over a considerable range, but the operating temperatures and pressures have one significant impact on the dimensions and cost of the components of the system. Depending on the intended use of the system, e.g. B. to drive vehicles, where it should have the smallest possible dimensions, or as stationary power machine, for example in private households,

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2806849

where the dimensions are not very critical, one will choose the design of the system, which then also the Ranges of permissible operating temperatures and operating pressures can be specified.

A large part of the usual energy sources is used for space heating and cooling. The subject matter of the invention can be used with particular advantage for these purposes. With the usual methods of space heating and cooling, the highest level of efficiency is achieved if a conventional air conditioning system with a compressor is used for cooling and the counterpart to this, the heat pump, is used for heating. It is by no means uncommon for the thermal energy delivered by such a system to be more than 2.5 times the shaft drive energy consumed. This process is essentially a circuit of the usual process for converting thermal energy into mechanical energy, because mechanical energy is suggested and heat is given off. Dor process is similar to jedocli do; r. The usual process for converting thermal energy into mechanical energy insofar as the working medium assumes a state with a low temperature and a high thermal energy content (T) and a state with a low temperature and a low thermal energy content (T ₀ ). In contrast to the usual process to convert thermal energy into mechanical energy, however, no useful power is emitted via the shaft, while the working fluid expanded between T ₁ and T ₃ the material used as an energy carrier is considerably reduced, so that the user also incurs

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Total costs for space heating and cooling reduced will,

In order to make the significance of the invention for combined refrigeration machines and heat pumps understandable, a conventional cold steam refrigeration machine will be briefly described below. (In contrast, it is serving for heating counterpart, the heat pump will not be described), the main components of such a chiller 300 are shown in Fig. K. They include a compressor 302, a condenser 306, an evaporator 306 and an expansion valve 308. The compressor 302 draws in a conventional refrigerant vapor which is under relatively low pressure. As a result, the pressure and temperature of the steam are increased to such values that it can give off heat to a coolant in the condenser 304. Generally, the steam in compressor 302 is superheated for this purpose. In the condenser 304, the superheated vapor is cooled with water or air as a coolant so that it becomes a saturated or supercooled liquid. This is supplied dom iqiansionsvontil 3O8 and throttled in this with essentially constant enthalpy to the evaporator pressure, whereby the saturation temperature of the liquid is reduced. At the same time, an unavoidable rapid evaporation of part of the liquid takes place, so that the flow emerging from the valve does not consist entirely of liquid. This rapid evaporation is an undesirable side effect of the expansion, because the vapor formed by the rapid evaporation has already absorbed ¥ ¥ ärmo and is practically useless as a refrigerant in the evaporator. The liquid-vapor mixture can be added directly to the

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2806849 • 34

Feed in damper 3O6 or in some cases also the Blow off steam to reduce the flow load on the evaporator. In both cases the evaporator will (or a room to be cooled) is supplied with a refrigerant under relatively low pressure. In the vaporizer 306, the liquid absorbs heat from the liquid to be cooled Space and evaporates the liquid, whereby saturated steam or superheated steam is formed, which is then in the next Cycle process is supplied to the compressor 302.

In Fig. 5 are the thermodynamic

Conditions for a basic cold steam refrigeration process, assumed to be ideal, shown in a temperature-entropy diagram. Of course, the ideal refrigeration process shown in Fig. 5 cannot be achieved in such precision, but one allows one to be assumed. ideal process, the determination of the optimum operating variables for comparison with practically executed systems In the ideal process will take place four thermodynamic processes which correspond to the operations explained with reference to Fig h.. For example, at a, the liquid refrigerant present along the route is subjected to expansion and thus an isentropic change and is thus converted into a liquid-vapor mixture. Isothermal heat is supplied to the refrigerant along the path bc, so that a desired cooling is effected. Point c applies to the case of dry compression, ie compression in which the compressor sucks in dry or somewhat superheated steam. Along the path cd, the vapor is isentropically compressed to a pressure which is so high that it can give off heat in the condenser along the path dea. First of all, along the route, the overheating heat is applied and then along the length

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the distance ea heat of vaporization. fed. It is believed that in this idealized process the heat absorption in the evaporator bc and the heat dissipation in the Condenser dea take place under constant pressure.

_{The one} supplied to the system in state T 1

Heat quantity Q ₁ represents a hatred for the refrigeration capacity figure of the refrigeration process and is represented in FIG. 5 by the area bczy. The amount of heat Q “given off in the state T“ is represented by the area deayz. The external work AJ required using an external energy source, which is represented by the area deabc, can therefore be expressed by the following equation:

A ₅ , - - (Q ₁ - Q ₂ )

This work becomes complete in a standard Kaltern machine performed by the compressor on the basis of the LSnorgie supplied to it.

As the refrigeration capacity figure ICLZ of a refrigeration machine, nan denotes the ratio that it generates Cold constricts to what is necessary to produce it Job:

For an idealized refrigeration process one can write:

KLZ =

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In practice, of course, you can't

achieve an ideal refrigeration process and the expansion or throttle valve does neither useful work nor can it Perform function without absorbing or dissipating heat through the walls of the tube or valve. the The function of a practically designed throttle valve is therefore better shown in FIG. 5 by the dashed line af shown. As the amount of cold generated by the system in the case of an ideal process through the area bczy and, in the case of throttling, the area fczx is, the area bfxy represents the loss of useful cooling compared to the ideal process.

An idealized throttling process that occurs when

constant enthalpy, ie is carried out adiabatically without work, has the known disadvantage that it does not take advantage of the possibility of recovering at least part of the compression work from the expanding refrigerant. If, for example, one were to use an expansion engine instead of a throttle valve, as has been proposed (see Kac-intire and co-workers:! Refrigeration Engineering, 2nd edition) and it would be said that the pressure in the expansion engine drops isentropically, as shown in Fig. 5, one could theoretically use a significant portion of the work done by the expanding refrigerants to drive the compressor. For this recovery of work, of course, the expense of the expansion engine must be accepted. From the point of view of energy saving, however, the replacement of a throttle valve by an expansion engine is a useful measure to improve the efficiency of the process or _o to

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Increase in the cooling capacity factor KLZ. This has apparently been recognized for many years, but so far it is apparently no refrigeration machine that works with high efficiency and high cost-effectiveness yet this theoretical possibility has been developed.

An expansion engine or turbine has, of course, been attempted (U.S. Patent 1,575,819 - Carrier; and U.S. Patent 2,519,010 - Zearfoss). However, the systems described in these patents are like all others Systems proposed up to now are not free from the disadvantages of throttling, but only take advantage of the fact that the flow rate of the working medium is increased by the throttling. For this purpose, a turbine is switched on in the flow path of the working medium, in which a. Leash ti ropes Sxiorgio dos working fluid is converted into mechanical energy part which are at least theoretically be used for the .iotriob the system lcann _o In this case, however, which enabled to perform work Nutzeiiergio that exiting in the from of a throttle device and includes a turbine trains leading working media is and is used for work in the turbine, only so little, so that the work done in this way is at most 30 -> the work that can theoretically be recovered. The work actually recovered is certainly not so great that the additional effort caused by the turbine could be amortized during a reasonable service life of the device through the energy saved.

In Fig. 6 a modified cold steam refrigeration machine of the usual type according to the invention is shown. That

809829/0521

Throttle valve is through an accelerating acting nozzle 320 and a turbine 322 have been replaced. The nozzle 320 increases the kinetic energy or speed of the refrigerant and causes this refrigerant to act on a correspondingly designed turbine 322 in which the refrigerant expands with cooling as well as in the throttle valve. From the known Systems, the present differs in that it is deliberately not throttled and that instead of a adiabatic expansion at constant enthalpy an expansion is brought about, which essentially or is at least approximately iso-tropic. To expand a fluid in a nozzle, the flow cross-section in constantly changed along the nozzle, so that the pressure and the speed of the fluid also changed x-zerdon. When it passes through the nozzle, the fluid is therefore on Nozzle outlet the highest speed and the lowest! ¥ eixn the speed of sound also locally is not achieved, throttling can be avoided. On the other hand, it usually occurs at the exit of capillary rings a throttling. It has been shown that with the same flow rates and the same inlet conditions Two-phase flow before exiting the nozzle a lower temperature and a higher speed than when exiting a capillary tube. If you use electricity for work, for example in a turbine, you can therefore increase the cooling capacity coefficient more by using a nozzle than by using a nozzle the use of a capillary tube. In the present embodiment one can get a much larger share use the expansion work advantageously to those for the operation of the compressor and fans and

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BAD ORSQiNAL

2806849

Pumps to reduce the external work required. Because so much more useful work is recovered in the present system As in the known systems, it is believed that the present system is economical in this respect is when the capital expenditure is amortized within a relatively short time by the energy saving.

If the expansion engine or turbine could actually be operated isentropically, then the dashed line ab in FIG. 7 would represent the expansion path of the refrigerant between the condenser and the evaporator. In practice, however, due to the turbine losses and other influences, isentropic operation cannot be achieved, so that the expansion in a turbine with an efficiency below 100 Ji is more realistically represented by the line ag Gczw shown «Since when using a nozzle and a turbine, a greater amount of cold Q _{1 is} generated than when using a throttle valve (area fczx) and since less external work A ^ is required, a higher refrigeration capacity figure is required

KLZ = ~

obtain. In FIG. H , the area gfzw shows the increase in the amount of cold produced due to the use of a nozzle and a turbine instead of a throttle valve.

In a practical embodiment

was used in a mechanical cold steam chiller as A commercially available fluorocarbon is used as the refrigerant,

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909829/0523

which occurred in liquid form at 4 ° C in the evaporator and "present in liquid form in the condenser at a temperature of 71 ° C at a total efficiency of the turbine and the compressor of 80 ^c / o there is the case of using a Throttle valve calculate the refrigeration capacity figure with IiLZ = 2.26 _o If, on the other hand, according to the invention, the throttle valve is replaced by a nozzle and a turbine, a refrigeration capacity figure KLZ of 3, o4 can be calculated, which means an improvement of about 3h yo

3s it is assumed that with assumed

Gerätewirlcungsgraden of 80 yo, a loss of about 3 h ρ of the "for the operation of the known cold vapor refrigerating machine theoretically foreign work required is due to the fact that a throttle valve is unable ₉ recover work of compression of a fluid and the recovery suzufüliren," If one of the nozzle and the turbine had a more realistic overall efficiency of about h ~. \ i antiimnt, which corresponds to the iiert already obtained experimentally, one can assume that about 2o \ j dor for de-i operation dor iZaltda:! r> f-Kaltoniasciu .no trcoretisch crforclorlicj.on -? randarboit from the. ', expanding on refrigerant nurücI -.' Tov / onnon word on can if one instead oinon Drossolvonxlls οinο nozzle and turbine used Given the many Iilliardon Hark, which annually for energy carriers be spent on space heating and -külilung, this saving is of 20 x, &fü'r the Federal territory a very considerable amount ₀ the au The capital outlay for a system of the usual type, provided with a nozzle and turbine according to the invention, with an air-conditioning machine or _a heat pump can be used for the individual consumers

- 27 -

■ 3? ·

be up to 10 .j higher than at present usual systems, but this additional effort is reduced by the expected energy savings in less than amortized in two years.

lian therefore recognizes that it has excellent results can be achieved by using a throttling-free nozzle or at least one nozzle that trots a possible under given starting conditions of the working medium Throttling allows a recovery of rael: .r work as a capillary tube or similar pressure reducing device, And if you have the Düso and the whole system like that interprets that instead of an enthalpy-constant operation, an approximately isentropic operation is obtained. The system works with operational quantities in which the pressure remains within the range of the saturation advantage, and the pressure of the Arbeitsinit fcols Tjird under Durclv-ang durcli don saturation pressure of the work equipment increased and decreased. That Work equipment can see cursor periods in plrysikalis States exist, clio ile, respective saturation conditions nicke correspond, 2. B. it can happen that oirie x-Müssigkoit iiic '.,'. t evaporates immediately when the pressure is below the seed fcigiinrswcrt sinks, uioso and other influences ! ■ .öimeii to actastabilor. Jediiir.xmgon and thus to one unregGlnaiLiiVGii and unregulated flow behavior Work equipment! 'Doors, Dsispiolsueiso it can happen that a liquid does not expand downstream, but radially or a phase change to an increase in volume and dadurcli to a reduction in the effective flow cross-section leads. Any such deviation from the desired operating behavior reduces the recovery of work from the system and thus its usage

- 28 -

S09829 / 0523

availability. Dalier in particular are said to be metastable
Avoid flow conditions _o Above
• were dalier means and measures to lift
metastable flow conditions described in the EUR

Another application of the present
Invention relates to the Verx ^ ending the EIIR for flow in safety valves, fluid containers _o This application does not necessarily lead to energy savings, railroad tank cars for the transport of
Hazardous substances, such as propane, butadiene ^ AmIUOnIaIc ₅ ethylene ^ vinyl chloride and the like ^ are provided with safety valves, which have a device to display an overpressure in the tank and a device that automatically opens the valve on the basis of an overpressure display opens so that the tank contents in a
Area which is under a lower pressure, usually into the environment. These valves are supposed to open when the pressure in the closed tank of the tanker reaches a predetermined level} which still
was below the bursting pressure of the tank An investigation into the causes of tanker accidents has shown that the dex-zeit safety valves used are unsuitable for their task because they are not up to the occurrence of two phases. These two phases occur ₉ when the tank contents boil violently after a tanker accident «This inability of the safety valves of tankers
for the effective delivery of two-phase currents with large
Flow rates and the fact that these safety valves are generally dimensioned too small, has to
Difficult problems led »According to the invention, a safety valve for a tanker now has a EUR,
which connects the tanker with the surrounding area ₉

- 29 -

909829 / 0S2

'"' 2806849

kv-

into which the tank line is to be dispensed with the safety valve open. Such a safety valve enables in the οίΎοιίΰ, α state o a delivery of large volumes of two-phase flows under predeterminable conditions. A ¥ UR provided in the manner described above with means for suppressing metastable flow conditions can be used with particularly great advantage in safety valves. Such a safety valve is intended to ensure maximum energy dissipation and a discharge of fluid box of high flow velocity and large flow rate. In this application of the EUR, it is therefore even more important than, for example, in refrigerating machines that there are no irregular flow conditions which could impair the fulfillment of these requirements. In particular, metastable flow conditions must not lead to a radial expansion taking place instead of a downstream one and that the effective flow cross section is reduced. When interpreting the EUR, its intended use must therefore be carefully observed.

Above, exemplary embodiments of

Invention described, which, however, can be modified within the scope of the inventive concept by a person skilled in the art.

809829/0523

Claims (1)

2808843 Claims; (ή. ivOxitiiiiiiorlicIiSG v ^r or, .- i "a ⁱ . ⁱ .i? on only bnvaiirilunf; voi \ ;; arm- ciior. '.' ic in nieclianiseize energy, dadurcli denotes, (a) that a stream of a working medium is generated, the aic "i in. a: - / · State oinor ir .: essential r-Goättir-toii -? lüssi 'koit is located and "thermal energy lind static.-iiier.'"; ie contains in a predetermined i · ciif-o,
(b) that at least ο in the tail of the genaniicon. "ner -; io des Ai-boitsmittelstroric converted into kinetic J.no?:riG and thereby becomes an otrorn 3rsou" t, which has a holie Gescliwindi. '.' lcoi fc and a lower ter.iporature and under oinom- ₍ - ^: .ο; ί · "Ί. · - ^^ · -τ) r..: α'1 ''.; r-cl: .oii .jn.viok ^r ; i: oht _f woi; ei das work equipment under this lower pressure, partly verdainD ± "t and dadurcii in dom current dos working medium a liainpi ¹ niiase _f: is eoildot, ⁽¹ U ₀₎ dal ^1, nin part of the pulse and the ¥ ärmeener" is dor UanroiftKiaso to the liquid: L-; o I'hase ü '.) Grtra "en and daclurc": the iJanrnfniaaso is condensed and Kur-t part Izonclonsiort and thereby a part ifirer Kondonsations-T / ärmo a: i gives the liquid Pliass, so that their speed, static pressure and temperature oriiöi? .t word on, (c) that obtained from the ZwoioJiasenstx-oin Jner ^ ie; and in 'ellenantriebsarboit is converted, (d) that thorn-date set out. electricity so much static _Jner: ~ ie su- ^ ofülirt is that the greater part condensed in the volume of the vapor phase of the current and dom current without evaporation of liquid at least required for the next cycle TJa.rmeonei -. ~ ie can be fed, - 31 - ■ a- (e) that the current exchanges heat with a heat source is subjected and thereby, by this Absorbs heat energy, and (f) that process steps (b) to (f) are repeated will. 2. Procedure after objection. 1, characterized in that the current is rolled into the liquid and vapor phase, before at least some of the static energy is supplied to him will. j. Process according to claim 2, characterized in that the vapor phase is compressed, the static pressure of the separated liquid phase is increased, the vapor phase and the liquid phase are mixed, the vapor condensing in the liquid, the static pressure The pressure of the liquid obtained by the mixing of the two phases is increased so much that it can be supplied with the required Iv ami em en-τ a, and that the liquid under increased pressure is exchanged with the '!,' arneensrgieauelle is subjected. I. The method according to claim 1, characterized in that as viärmesnerrie a Urü ^ G'ran-saiTQrnisträ.jrer is used. '- .. ancestors according to claim ^! , characterized in that the atmosphere or water or waste heat are used as ambient energy. 6. The method according to claim 1, characterized in that for converting said part of the energy of the working medium flow into kinetic energy, the working medium in the state of a substantially saturated liquid is passed through at least one Vercington flow cross-section . - 32 - 909820/052 $ 7. Ancestors according to claim 6, dadurcli gekemselehnet that The working medium flow through several narrowed flow cross-sections is performed, the static pressure of the working medium in each of these narrowed flow cross-sections is lower than in the narrowed flow cross-sections upstream thereof. δ. Ancestors according to claim 7, characterized in that the narrowed ütröraunrsquersclniitts in the direction of coronation are arranged at a distance from each other. 9. VerfaJiren according to claim 6, characterized in that the work equipment through several in the direction of the flow narrowing stretches and stretches arranged between them and widening flow lines and the static pressure in each of these narrowing or expanding sections is lower than in the upstream from it located, narrowing or widening routes. 10. The method according to claim 6, characterized in that to suppress metastable flow conditions in the narrowed flow cross-section, the flow in this ge st öi-1. 11. The method according to claim 8, characterized in that for suppressing metastable flow conditions in the narrowed flow cross-sections, the flow in these is disturbed. 12. VerfaJiren according to claim 11, characterized in that for disrupting and slowing down the flow of the working medium flow a second fluid stream is fed to this. - 33 - 9829/0523 2906843 13 · The method according to claim 11, characterized in that to disrupt the flow of the working medium flow this is subjected to the action of mechanical means. 14. The method according to claim 11, characterized in, that to disturb the flow of the working medium flow on this wave energy is brought into action, Method according to Claim 1, characterized in that the static energy content of the working medium flow is increased by the supply of static energy in step (d) to at least the amount determined in accordance with step (a). 16. The method according to claim 6, characterized in that Carbon dioxide, liquid nitrogen or a fluorocarbon is used as the working medium. 17. The method according to claim 17 »characterized in that that difluoromonochloromethane, pentafluoromonochloroethane, Difluorodichloromethane or a mixture thereof as Work equipment is used. 18. Heating or cooling process in which a vaporous refrigerant compressed and condensed and the resulting refrigerant flow to lower its saturation temperature and its saturation pressure is subjected to expansion and the expanded refrigerant stream to heat exchange is subjected to a thermal energy source and thereby at least partially evaporated, thereby characterized in that the refrigerant flow to its expansion - 3k - 909825/0523 guided essentially free of throttling through at least one narrowed flow cross-section and thereby the kinetic energy of the refrigerant flow is increased and that the kinetic energy of the expanded refrigerant flow then converted into shaft drive work xvird. 19. The method according to claim 18, characterized in that that the refrigerant flow is in the state of an essentially saturated liquid before its expansion is located. 20. The method according to claim 18, characterized in that to convert the kinetic energy into shaft drive work, the expanded refrigerant flow through an expansion engine to be led. 21 · Method according to claim 18, characterized in that to suppress metastable flow conditions in the narrowed flow cross-section, the flow in this is disturbed. 22. The method according to claim 21, characterized in that to disturb the flow in the narrowed flow cross-section mechanical means are brought into effect in this. 23. The method according to claim 21, characterized in that to disrupt the flow in the narrowed flow cross-section in this wave energy on the refrigerant flow is brought into action » 2k, method according to claim 21, characterized in that a second fluid flow is supplied to disrupt the flow of the refrigerant flow. ~ * 35 ⁼ 25. Procedure according to. Claim 18, characterized in that that the refrigerant flow is passed through several narrowed flow cross-sections, the static pressure of the Refrigerant in each of these narrowed flow cross-sections is lower than in the narrowed flow cross-sections upstream thereof. 26. The method according to claim 25, characterized in that the narrowed flow cross-sections are arranged at a distance from one another in the flow direction. 27. The method according to claim 18, characterized in that the refrigerant is guided through several stretches narrowing in the direction of flow and, arranged between them, stretches widening in the direction of flow, and the static pressure in each of these narrowing or widening stretches is lower than in the upstream from it located, narrowing or widening routes. 28. The method according to claim 26, characterized in that to suppress metastable flow conditions in the narrowed flow cross-section, the flow in this -restort will. 29. Verfaliren according to claim 28, characterized in that that in order to disturb the flow of the refrigerant flow it is subjected to the action of mechanical means. 30. The method according to claim 28, characterized in that to disturb the flow of the cold emitter on these Wave energy is brought into action. - 36 - 31. The method according to claim 28, that for disrupting the flow of the refrigerant flow is supplied to a second fluid flow will. 32. The method according to claim 19, characterized in that that the refrigerant flow to its expansion through several narrowed flow cross-sections are guided, which are arranged at a distance from one another in the direction of flow, that to suppress metastable flow conditions in the narrowed flow cross-sections the flow is disturbed in these and that the expanded refrigerant flow to convert the kinetic energy into shaft drive work is passed through an expansion engine. 33 · Steam powered mechanical heating or cooling system for Carrying out a cycle with a compressor to increase the temperature and pressure of a stream a vapor refrigerant, a condenser for cooling the flow of vapor refrigerant into the State of a substantially saturated liquid, an expansion device for expanding the flow of the liquid refrigerant with lowering of a saturation temperature and pressure and an evaporator to carry out a heat exchange between a poor energy source and the expanded stream, see above that this at least partially evaporates, characterized in that the expansion device is an energy conversion device with at least one essentially throttling-free nozzle section, which is used to to increase the kinetic energy of the refrigerant flow, as well as an expansion engine. to convert the kinetic energy of the refrigerant flow in shaft drive work. - 37 - 809829/0523 3k, system according to claim. 33, characterized in that the nozzle section has a narrowed flow cross-section. 35. System according to. Claim 33, characterized by a Interference arrangement for suppressing metastable flow conditions in the energy conversion device. 36. System according to claim 35 »characterized by a mechanical device arranged in the flow path of the refrigerant to disturb the flow. 37 · System according to claim 35 »characterized by means for charging the refrigerant flow with Yolloiien energy. 3Ö. S3 ^r steni according to claim 35 »characterized by a device for supplying a second fluid flow to the refrigerant flow. 39. System according to claim 33 »characterized in that the iCnergieumwandlungseinrichtung several at a distance from each other has arranged nozzle lines. / + O. System according to claim 39 »characterized in that the Düson stretches a plurality of narrowed cross-sectional flow lines arranged at a distance from one another in the direction of flow each of which is smaller than the narrowed flow cross-sections located upstream thereof. kl. System according to claim. 39 », characterized in that the nozzle sections have a plurality of narrowed flow cross-sections arranged at a distance from one another in the flow direction, each of which is larger than the narrowed flow cross-sections arranged upstream thereof. - 38 - Ö09829 / 0523 42. System according to claim 33, characterized in that the energy conversion ^ facility several themselves in the Paths narrowing the direction of flow and arranged between them and expanding in the direction of flow Has stretching. 43. System according to claim 42, characterized in that the stretches narrowing in the direction of flow, nozzle stretches and widening in the direction of flow © Sections are diffuser sections and the first section of the energy conversion device is a nozzle section » 44. System according to claim 42, characterized in that the stretches narrowing in the direction of flow Diffuser sections and which are in the direction of flow expanding sections are nozzle sections and the first section of the energy conversion device is a nozzle section is. 45. System according to claim 39 »characterized in that in the energy converter for suppressing metastable flow conditions means of disrupting the Flow are arranged. 46. System according to claim 45, characterized in that in the iCnorgio converter mechanical means for Disrupting the flow are arranged. 47. System according to claim 46, characterized in that means for applying wave energy to the refrigerant flow are provided. 48. System according to claim 46, characterized in that a Means for supplying a second Fluidstronis to the - 39 - -AO- Refrigerant flow is provided. M-9. Safety valve for relieving a fluid storage container from an overpressure due to the delivery of a multi-phase positive current to a lower pressure surrounding area, characterized by (a) means for indicating an overpressure in the
Container, (b) a device for automatically opening the safety valve, Lim an outflow of the fluid from the
Allow container and (c) a conduit which has a flow channel between the
Container and the surrounding area forms and at least one substantially throttling-free nozzle section having. 50. Safety valve according to claim h9, characterized in that for Unterdiüickung metastable flow conditions in the flow channel in this mechanical means for
are arranged otöron the flow. ^ 1, safety valve according to claim 49, characterized in that the line several spaced apart
That ens ti "o cken oosibst. 32. Safety valve according to claim 51, characterized in that the nozzle sections have a plurality of narrowed flow channels arranged at a distance from one another in the flow direction. have cross-sections, each of which is smaller than _t : the narrowed flow cross-sections located upstream thereof. 53. Safety valve according to claim 51 »characterized in that since the nozzles stretch several in the direction of flow 009829/0523 3ADORlQiNAL 28068 * 3 Have spaced-apart, narrowed flow cross-sections, each of which is larger than that constricted flow cross-sections arranged upstream thereof. 5 ^. Safety valve according to claim 49, characterized in that that the line several itself in the direction of flow has narrowing stretches and stretches arranged between them and widening in the direction of flow. 55 · Safety valve according to claim hS , characterized in that the sections narrowing in the flow direction are dry and the sections widening in the direction of flow are diffuser sections and the first section of the line is a nozzle flow. 56. SichorJioitsventil according to Anspx-uch 5``> characterized in that the stretches narrowing in the direction of flow Diffuser stretches and the sicii in the direction of flow expanding stretches of nozzles are and the first Section of the line is a nozzle section. 57. Safety valve according to claim 5I, characterized in that that zux 'suppression of metastable flow conditions in the flow channel in this mechanical means for disrupting the flow are arranged. 909829/0523